JP2008298265A - Two-way clutch unit - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent gearing mismesh of a dog in a dog clutch for a moment load applied to an output shaft from the load side. <P>SOLUTION: A two-way clutch unit comprises an input outer ring 10 rotationally driven by a drive source, an output shaft 20 for taking out of the torque transmitted from the input outer ring 10 to the outside, a clutch ring 30 disposed between the input outer ring 10 and the output shaft 20 axially movably and not relatively rotatably, capable of engaging/disengaging with the output shaft 20, and a cam mechanism 40 for controlling the engagement/disengagement of the clutch ring 30 and the output shaft 20 by axially moving the clutch ring 30 with the circumferential movement. A roller bearing 1 is disposed between a housing 51 and the output shaft 20. The elastic force of a coil spring 4 and the elastic force of a coil spring 5 are made balanced in a state where dogs 34, 83 of the dog clutch 2 are meshed with each other to the deepest portion. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention is used, for example, in an open / close mechanism such as an electric slide door, an electric back door, an electric curtain, and an electric shutter in a power window of an automobile, a one-box car, and a torque from an input system to an output system when a drive source is operated. The present invention relates to a two-way clutch unit that transmits and interrupts transmission of torque when a drive source is stopped to enable manual operation of an output system.

  For example, there is an electric slide door device for an automobile (one box car) in which a drive motor and a slide door are connected or disconnected by a two-way clutch unit. The two-way clutch unit has a structure in which input and output are connected and disconnected by a cam mechanism (see, for example, Patent Document 1). FIG. 11 shows a schematic configuration of the 2-way clutch unit disclosed in Patent Document 1.

  The two-way clutch unit includes an input outer ring 110 that is rotationally driven by a drive motor, an output shaft 120 that extracts rotational torque transmitted from the input outer ring 110 to the outside, and an input outer ring 110 and an output shaft 120 interposed between the input outer ring 110 and the output shaft 120. A clutch ring 130 that can be engaged with and disengaged from the output shaft 120, and a cam mechanism 140 that controls engagement and disengagement between the clutch ring 130 and the output shaft 120 by moving the clutch ring 130 in the axial direction. It has.

  Each component including the input outer ring 110, the output shaft 120, the clutch ring 130, and the cam mechanism 140 is accommodated in a housing 150 that is a stationary member, and the housing 150 that accommodates each component is flattened via an intermediate side plate 152. It is integrated by attaching to the attachment side board 154 of a shape. When this clutch unit is incorporated in an electric slide door device, the input outer ring 110 is connected to a drive motor, the output shaft 120 is connected to a slide mechanism for opening and closing the slide door, and the mounting side plate 154 is electrically slid by bolting or the like. It is attached to a fixed part (not shown) of the door device.

  The cam mechanism 140 is configured such that the fixed cam 142 pressed against the mounting side plate 154 by an elastic member 160 such as a wave spring and the axial engagement of the fixed cam 142 causes the clutch ring 130 to move in the axial direction via the coil spring 170. The movable cam 144 is moved. The fixed cam 142 is pressed against the mounting side plate 154 by the elastic force of the elastic member 160 interposed between the intermediate side plate 152 and the fixed cam 142 described above, and the rotational resistance between the end surface of the fixed cam 142 and the mounting side plate 154 is reduced. Is generated.

  Further, a dog clutch 180 is formed on the clutch ring 130 and the output shaft 120, and the clutch shaft 130 is engaged with the dogs 182 and 184 in the dog clutch 180 by the axial movement of the clutch ring 130 to the left in the figure. 130 is engaged. Due to the engagement between the clutch ring 130 and the output shaft 120, the rotational torque of the input outer ring 110 is transmitted to the output shaft 120 via the clutch ring 130, and the door can be opened and closed electrically.

  At this time, the movable cam 144 rotates with the input outer ring 110, and the fixed cam 142 receives the rotational force from the movable cam 144 and rotates the same, but receives the rotational resistance from the mounting side plate 154 due to the pressing of the elastic member 160. The axial force is transmitted to the movable cam 144 by the rotational resistance.

On the other hand, a coil spring 190 is interposed between the clutch ring 130 and the output shaft 120, and an elastic force is urged so as to separate the two from each other. Due to the elastic force of the coil spring 190, when the drive motor is stopped, the clutch ring 130 is pressed to the right side in the drawing and is separated from the output shaft 120. Therefore, the dog clutch 180 of the output shaft 120 and the clutch ring 130 The dogs 182 and 184 are not engaged with each other. Thus, since the dog 182 of the output shaft 120 and the dog 184 of the clutch ring 130 are not engaged with each other, the output shaft 120 is free to rotate from the output shaft side, and the door can be manually operated. Can be opened and closed freely.
JP 2005-172141 A

  By the way, in the conventional 2-way clutch unit disclosed in Patent Document 1, the output shaft 120 is inserted into the cylindrical portion 156 by inserting the output shaft 120 through the small-diameter cylindrical portion 156 formed at the end of the housing 150. The inner diameter surface is supported in a sliding state. Such a structure is simple, inexpensive, and effective for cost reduction. However, the output shaft 120 is axially applied to a moment load input from the load side such as a slide mechanism to which the output shaft 120 is coupled. The clutch ring 130 and the cam mechanism 140 may become unstable.

  That is, when the output shaft 120 is inclined with respect to the axial direction, the dog clutch 180 constituted by the output shaft 120 and the clutch ring 130 is in a state where the output shaft 120 is inclined with respect to the clutch ring 130. A meshing failure or abnormal noise occurs between the dog 182 of the shaft 120 and the dog 184 of the clutch ring 130. Due to the poor meshing of the dogs 182 and 184 in the dog clutch 180, the operation of the clutch ring 130 and consequently the operation of the movable cam 144 and the fixed cam 142 of the cam mechanism 140 become unstable.

  Accordingly, the present invention has been proposed in view of the above-described problems, and the object of the present invention is to prevent a dog meshing failure in a dog clutch against a moment load applied to the output shaft from the load side. To provide a clutch unit.

  As technical means for achieving the aforementioned object, the present invention provides a stationary system member, an input system rotation member that is rotationally driven by a drive source, and a torque transmitted from the input system rotation member. An output system rotating member, a torque transmitting member that is axially movable between the input system rotating member and the output system rotating member and that cannot be relatively rotated, and that can be engaged with and disengaged from the output system rotating member, and stationary A two-way clutch unit including a control member that controls engagement / disengagement between a torque transmission member and an output system rotation member by moving the torque transmission member in an axial direction through relative angular displacement with respect to the system member. It is characterized by.

  (1) A rolling bearing is interposed between the stationary system member and the output system rotating member.

  (2) A dog clutch in which dogs are respectively formed in the axially opposed portions of the torque transmission member and the output system rotating member, and the dog is engaged and disengaged with the output system rotating member by the axial movement of the torque transmitting member. And a first elastic member between which the elastic force is urged in a direction to separate the two members from each other between the torque transmission member and the output system rotation member, and between the torque transmission member and the control member. A second elastic member that is urged coaxially with the elastic force of the first elastic member in a direction to separate the two members from each other, and the elastic force of the first elastic member and the second elastic member The elastic force of the elastic member is balanced in a state where the dogs of the dog clutch are engaged to the innermost part.

  (3) A rolling bearing is interposed between the stationary system member and the output system rotating member, and dogs are respectively formed in the axially opposed portions of the torque transmitting member and the output system rotating member. A dog clutch that engages and disengages the dog with the output system rotating member is formed by the movement, and the elastic force is biased between the torque transmitting member and the output system rotating member in a direction to separate the two members from each other. A second elastic member is interposed between the torque transmitting member and the control member, and an elastic force is urged coaxially with the elastic force of the first elastic member in a direction to separate the two members from each other. These elastic members are interposed, and the elastic force of the first elastic member and the elastic force of the second elastic member are balanced in a state where the dogs of the dog clutch are engaged to the innermost part.

  In the present invention, since the rolling bearing is interposed between the stationary system member and the output system rotating member, the output system rotating member is subjected to the rolling bearing with respect to the moment load input to the output system rotating member from the load side. Therefore, it is possible to prevent the output system rotating member from being inclined. As a result, engagement / disengagement between the torque transmission member and the output system rotation member can be reliably performed.

  In the present invention, the elastic force of the first elastic member and the elastic force of the second elastic member are balanced in a state where the dogs of the dog clutch are engaged with each other to the innermost part, so that the output from the load side is achieved. Even if the output system rotating member is inclined with respect to the torque transmission member with respect to the moment load input to the system rotating member, the elastic force of the first elastic member and the elastic force of the second elastic member are balanced. When the dogs are engaged with each other, that is, when the dogs are engaged with each other in the dog clutch constituted by the output system rotating member and the torque transmission member, the dogs are engaged with each other up to the innermost portion, so that the engagement failure of the dogs can be prevented. As a result, engagement / disengagement between the torque transmission member and the output system rotation member can be reliably performed.

  Further, according to the present invention, a rolling bearing is interposed between the stationary system member and the output system rotating member, and the dogs of the dog clutch are configured such that the elastic force of the first elastic member and the elastic force of the second elastic member are By balancing in a state where the innermost part is engaged, the output system rotating member can be firmly supported by the rolling bearing against the moment load input to the output system rotating member from the load side. It is possible to prevent the output system rotating member from being inclined. On the other hand, even when the output rotating member is tilted with respect to the torque transmission member with respect to the moment load that cannot be supported by the rolling bearing, the dogs are engaged with each other to the innermost part when the dogs are engaged with each other. As a result, it is possible to prevent the dog from meshing poorly. As a result, engagement / disengagement between the torque transmission member and the output system rotating member can be performed more reliably.

  In the present invention, a structure in which a plurality of rolling bearings interposed between the stationary system member and the output system rotating member are arranged along the axial direction of the output system rotating member is preferable. If the output system rotating member is supported with respect to the stationary system member by a plurality of rolling bearings in this way, a structure that is strong against the moment load input to the output system rotating member from the load side can be realized. Inclination can be prevented more reliably. A ball bearing is suitable as the rolling bearing.

  The two-way clutch unit of the present invention can be applied by being incorporated in an electric slide door device by connecting an input system rotating member to a drive motor and connecting an output system rotating member to a door slide mechanism. . In this case, by controlling the engagement / disengagement between the torque transmission member and the output system rotation member, when the drive motor and the slide door are connected, an electric opening / closing operation is possible, and when the drive motor and the slide door are not connected, Manual opening and closing operations are possible.

  In the present invention, since the rolling bearing is interposed between the stationary system member and the output system rotating member, the output system rotating member is subjected to the rolling bearing with respect to the moment load input to the output system rotating member from the load side. Therefore, it is possible to prevent the output system rotating member from being inclined. As a result, the torque transmission member and the output system rotating member can be reliably engaged and disengaged, the operation stability of the clutch can be ensured, and the reliability can be improved. Further, by using a rolling bearing, it is possible to reduce the torque loss during rotation, and it is easy to contribute to downsizing of the drive source.

  In the present invention, the elastic force of the first elastic member and the elastic force of the second elastic member are balanced in a state where the dogs of the dog clutch are engaged with each other to the innermost part, so that the output from the load side is achieved. Even if the output system rotating member is inclined with respect to the torque transmission member with respect to the moment load input to the system rotating member, the dogs are engaged with each other to the innermost part when the dog is engaged in the dog clutch. , It is possible to prevent the dog from being poorly meshed. As a result, the torque transmission member and the output system rotating member can be reliably engaged and disengaged, the operation stability of the clutch can be ensured, and the reliability can be improved.

  Further, according to the present invention, a rolling bearing is interposed between the stationary system member and the output system rotating member, and the dogs of the dog clutch are configured such that the elastic force of the first elastic member and the elastic force of the second elastic member are By balancing in a state where the innermost part is engaged, the output system rotating member can be firmly supported by the rolling bearing against the moment load input to the output system rotating member from the load side. It is possible to prevent the output system rotating member from being inclined. On the other hand, even if the output rotation member tilts with respect to the torque transmission member with respect to the moment load that cannot be supported by the rolling bearing, the dogs are engaged to the innermost part when the dogs are engaged with each other. As a result, it is possible to prevent the dog from meshing poorly. As a result, the engagement / disengagement between the torque transmission member and the output system rotating member can be performed more reliably, the operation stability of the clutch can be sufficiently ensured, and the reliability can be dramatically improved. .

  Hereinafter, an embodiment in which the two-way clutch unit according to the present invention is applied to, for example, an electric sliding door device of an automobile (one box car) will be described in detail.

  The clutch unit of the embodiment shown in FIG. 1 has an input outer ring 10 as an input system rotating member that is rotationally driven by a drive motor as a driving source, and an output system rotation for extracting torque transmitted from the input outer ring 10 to the outside. An output shaft 20 as a member, a clutch ring 30 as a torque transmitting member that is interposed between the input outer ring 10 and the output shaft 20 and can be engaged / disengaged with the output shaft 20, and the clutch ring 30 and the output shaft It is comprised by the principal part which consists of the cam mechanism 40 as a control member which controls engagement / disengagement with 20.

  The input outer ring 10 has a hollow shape, and the output shaft 20, the clutch ring 30 and a part of the cam mechanism 40 are accommodated in the input outer ring 10, and is a stationary member on the opposite side of the input outer ring 10 from the output shaft 20. The cover 50 is disposed, the input outer ring 10 is surrounded by the cover 50 from the outside, and the input outer ring 10 and the cover 50 are connected by a spacer 60.

  When this clutch unit is incorporated in an electric slide door device, the input outer ring 10 is connected to a drive motor, the output shaft 20 is connected to a slide mechanism that opens and closes the slide door, and the cover 50 is electrically driven by bolting or the like. It is attached to a fixed part (not shown) of the device.

  As shown in FIGS. 1 and 2 (a) and 2 (b), the input outer ring 10 has a hollow, substantially cylindrical shape, and a worm wheel 12 is formed on the outer periphery of one end thereof. The worm wheel 12 meshes with a worm (not shown) that is rotationally driven by a drive motor (not shown) to constitute a worm gear. In addition, as a power transmission mechanism between the drive motor and the input outer ring 10, it is also possible to employ a winding transmission device in addition to the gear illustrated in the drawings.

  A flange portion 14 for fixing the output shaft 20 is formed on the inner diameter of the input outer ring 10. In addition, an annular groove 16 is formed on the outer diameter of the input outer ring 10 as a recess to which a claw-like projection 66 (described later) of the spacer 60 is locked.

  As shown in FIGS. 1, 3 (a), 3 (b), and 4 (a) and 4 (b), the output shaft 20 includes two members, a shaft member 70 and a dog member 80, and a shaft hole 82 of the dog member 80. The shaft member 70 is inserted into the shaft member 70, and the cross-shaped portion 72 formed at one end of the shaft member 70 is fitted into the cross-shaped recess 84 communicating with the shaft hole 82 of the dog member 80. Yes.

  A flange portion 86 is formed on the outer diameter of the dog member 80. The flange portion 86 is positioned by pressing the flange portion 86 against the flange portion 14 of the input outer ring 10, and a concave groove 88 formed on the outer diameter of the dog member 80. By inserting the retaining ring 81 into the dog member 80, the dog member 80 is prevented from coming off.

  On the other hand, by inserting the retaining ring 76 into the concave groove 74 formed on the outer diameter of the shaft member 70, the rolling bearing 1 such as a ball bearing is sandwiched between the retaining ring 76 and the dog member 80. The shaft member 70 is secured to the dog member 80 by the retaining ring 76.

  The output shaft 20 is rotatably supported via a rolling bearing 1 on a housing 51 (a stationary part of the electric slide door device) that is a stationary member. The output shaft 20 is connected to the slide mechanism by a spline 78 formed on the outer diameter of the shaft member 70.

  As described above, by providing the rolling bearing 1 between the housing 51 and the output shaft 20, the rolling bearing 1 supports the output shaft 20 against the moment load input to the output shaft 20 from the load side. Since it can support firmly, it can prevent the output shaft 20 inclining with respect to the clutch ring 30 beforehand. As a result, engagement / disengagement between the clutch ring 30 and the output shaft 20, that is, engagement of the dogs 34 and 83 in the dog clutch 2 described later can be reliably performed, and the operation stability of the dog clutch 2 can be ensured.

  In this embodiment, the output shaft 20 is supported by the single rolling bearing 1 with respect to the housing 51. However, the two rolling bearings 1 can be arranged in tandem in the axial direction. In this way, the structure can be made stronger against the moment load. The number of axial arrangements of the rolling bearing 1 is arbitrary.

  A plurality of dogs 83 are provided on the end surface of the dog member 80 of the output shaft 20 facing the clutch ring 30, that is, on the end surface of the flange portion 86. In this embodiment, the case where eight dogs 83 are arranged on the dog member 80 of the output shaft 20 at equal intervals in the circumferential direction is illustrated, but the number of the dogs 83 is arbitrary.

  The clutch ring 30 is slidable in the axial direction with respect to the input outer ring 10 and is mounted so as not to be relatively rotatable. That is, a plurality of (four) concave grooves 18 along the axial direction are formed at equal intervals in the circumferential direction on the inner diameter of the input outer ring 10 (see FIG. 2B), and a clutch ring corresponding to this is formed. As shown in FIGS. 5A and 5B, convex portions 32 that fit into the concave grooves 18 are formed at equal intervals in the circumferential direction on the outer diameter of 30. The convex portion 32 has a column shape extending in the axial direction toward the cam mechanism 40. By adopting such a structure, the clutch ring 30 is slidable in the axial direction with respect to the input outer ring 10 and is not relatively rotatable (can rotate together with the input outer ring 10).

  A plurality of dogs 34 are provided on an end surface of the clutch ring 30 facing the dog member 80 of the output shaft 20, and the dog clutch 2 is formed by the dog 83 of the output shaft 20 described above. In this embodiment, the case where eight dogs 34 are arranged on the clutch ring 30 at equal intervals in the circumferential direction is illustrated. However, the number of the dogs 34 is arbitrary, and the dogs of the output shaft 20 are arranged. The number may be equal to 83.

  Further, in the dog clutch 2 composed of the dog 34 of the clutch ring 30 and the dog 83 of the output shaft 20, the dogs 34 and 83 are repeatedly engaged with each other. Therefore, a lubricating oil such as grease is used to improve durability. Is applied. Therefore, a groove 38 is formed on the surface of the clutch ring 30 facing the dog member 80 of the dog 34 for the purpose of facilitating disengagement from the meshed state with the dog member 80 and improving operability. The groove 38 reduces the contact area with the dog member 80.

  The clutch ring 30 moves in the axial direction toward the side close to the output shaft 20 so that the dog 34 of the clutch ring 30 meshes with the dog 83 of the output shaft 20, that is, each dog 34 of the clutch ring 30 is engaged with the output shaft 20. When the dog 34 and the dog 83 are brought into contact with each other in the rotational direction by being arranged between the dogs 83, both are integrated in the rotational direction and torque is transmitted. Further, when the clutch ring 30 moves away from the output shaft 20 along the axial direction from the meshed state and the dog 34 of the clutch ring 30 is detached from the dog 83 of the output shaft 20, the two are separated and torque is increased. Is cut off.

  As shown in FIGS. 1, 3 (a), 3 (b) and FIGS. 5 (a), 5 (b), the output shaft 20 and the clutch ring 30 are implanted in the central concave hole 71 of the shaft member 70 of the output shaft 20. The support shaft 3 is inserted into the central through hole 36 of the clutch ring 30 so as to be coaxially disposed, and the clutch ring 30 can move in the axial direction with respect to the output shaft 20.

  In addition, a coil spring 4 as a first elastic member is interposed between the shaft member 70 of the output shaft 20 and the clutch ring 30, and an elastic force is biased in a direction to separate them from each other. The elastic force of the coil spring 4 prevents the clutch ring 30 and the output shaft 20 from meshing when the drive motor is stopped.

  The urging force that separates the clutch ring 30 and the output shaft 20 by the coil spring 4 is stopped when the clutch ring 30 moves in the axial direction and the tip end in the axial direction of the convex portion 32 contacts the fixed cam 90. . As a result, the amount of movement by which the clutch ring 30 is separated from the output shaft 20 is restricted.

  As shown in FIGS. 1, 6 (a), 6 (b) and 7 (a), 7 (b), the cam mechanism 40 disposed on the opposite side of the output shaft 20 across the clutch ring 30 is provided with a fixed cam 90 [ 6 (a) and 6 (b)] and a movable cam 100 (see FIGS. 7 (a) and 7 (b)). A coil spring 5 is interposed between the movable cam 100 and the clutch ring 30 as a second elastic member that urges the elastic force in a direction to separate them from each other.

  Further, like the clutch ring 30, the support shaft 3 planted in the central concave hole 71 of the shaft member 70 of the output shaft 20 is coaxially disposed by being inserted into the central through hole 102 of the movable cam 100, and fixed cam The movable cam 100 is movable in the axial direction with respect to 90. The support shaft 3 is supported by being fitted into the central concave hole 92 of the fixed cam 90.

  The movable cam 100 is slidable in the axial direction with respect to the input outer ring 10 and is mounted so as not to be relatively rotatable. That is, the outer diameter of the movable cam 100 is made to correspond to a plurality (four pieces) of the concave grooves 11 (see FIG. 2B) formed along the axial direction at equal intervals in the circumferential direction on the inner diameter of the input outer ring 10. A plurality of (four) convex portions 104 that fit into the concave grooves 11 are formed at equal intervals in the circumferential direction. Thereby, the movable cam 100 is slidable in the axial direction with respect to the input outer ring 10 and is not relatively rotatable (can rotate together with the input outer ring 10).

  As shown in FIGS. 6A and 6B, the end surface of the fixed cam 90 facing the movable cam 100 is formed of an inclined surface 96 and a flat surface 98, and can be fitted to the movable cam 100 in the axial direction. The surface 91 is protrudingly provided. On the other hand, the end surface of the movable cam 100 facing the fixed cam 90 is composed of an inclined surface 106 and a flat surface 108 as shown in FIGS. The cam surface 101 that can be fitted is recessed.

  On the other hand, in this clutch unit, the input outer ring 10 and the cover 50 contain each component including the output shaft 20, the clutch ring 30 and the cam mechanism 40, and the input outer ring 10 and the cover 50 are interposed via the spacer 60. Connected structure. A wave washer 6 is interposed between the fixed cam 90 of the cam mechanism 40 and the spacer 60 (see FIG. 1).

  The wave washer 6 presses the fixed cam 90 against the cover 50, and rotational resistance is applied between the cover 50 and the fixed cam 90. By providing a recess 93 on the surface of the fixed cam 90 facing the cover 50, the contact area is reduced to give a desired rotational resistance (see FIG. 6B).

  As shown in FIGS. 8A and 8B, the cover 50 has a bottomed cylindrical shape, and the fixed cam 90 of the cam mechanism 40 is accommodated in the recess 52 formed in the bottom of the cylindrical portion 54 (see FIG. 8). 1). In addition, a plurality of (four) concave holes 56 are formed at equal intervals in the circumferential direction at a portion between the concave portion 52 and the cylindrical portion 54 described above.

  A plurality (three) of flange portions 58 are formed at the opening end of the cylindrical portion 54, and the fixing portion of the electric slide door device (see FIG. The clutch unit is assembled by attaching to (not shown).

  On the other hand, as shown in FIG. 1 and FIGS. 9A and 9B, the spacer 60 is inscribed in the cylindrical portion 54 of the cover 50 that is a stationary member, and is inserted into a recessed hole 56 formed in the cover 50. An outer cylinder portion 64 having a claw-like projection 62 to be locked, and an inner cylinder portion 68 having a claw-like projection 66 circumscribed by the input outer ring 10 and locked to the groove 16 formed in the input outer ring 10. The outer cylinder portion 64 and the inner cylinder portion 68 are connected to each other. In addition, the rigidity of the spacer 60 is ensured by forming a plurality of triangular ribs 63 at equal intervals in the circumferential direction in the connecting portion 61.

  By adopting such a structure, the claw-like projections 62 of the outer cylindrical portion 64 of the spacer 60 are inserted into the concave holes 56 of the cover 50 while being elastically deformed radially inward, and then the concave holes are formed by the elastic restoring force. 56, the claw-like projection 66 of the inner cylinder portion 68 is elastically deformed radially outward, and the elastic restoring force is used to engage the concave groove 16 of the input outer ring 10, The cover 50 and the input outer ring 10 can be easily connected by the spacer 60.

  An operation example of the two-way clutch unit of the embodiment having the above-described configuration will be described in detail below.

  When the drive motor is stopped, the fixed cam 90 and the movable cam 100 are in a neutral state in which the flat surfaces 98 and 108 are in contact with each other, so that the movable cam 100 is fixed by the elastic force of the coil spring 5. The cam 90 is in contact with the cam 90. Further, the clutch ring 30 is biased in a direction away from the output shaft 20 by the elastic force of the coil spring 4, and is regulated at a position where it is separated from the dog 83 of the output shaft 20.

  Since the dog 34 of the clutch ring 30 and the dog 83 of the output shaft 20 are not engaged with each other in this way, the output shaft 20 is free to rotate from the output shaft side, and the door is manually operated. Can be opened and closed freely.

  On the other hand, when the drive motor rotates, the input outer ring 10 starts to rotate via the worm gear, and the rotational force of the drive motor is transmitted to the input outer ring 10 at a reduced speed by the worm gear. The movable cam 100 is regulated in the rotational direction by being concavo-convexly fitted to the input outer ring 10 by a concave groove 11 (see FIG. 2B) and a convex portion 104 (see FIGS. 7A and 7B). Therefore, it rotates with the input outer ring 10.

  On the other hand, since the fixed cam 90 is fixed in the rotation direction by the rotation resistance by the wave washer 6, the above-described movable cam 100 is the cam surface 101 that fits the fixed cam 90, that is, the inclined surface. It rotates along the line 106 and moves to the output shaft side along the axial direction by the rotation.

  As the movable cam 100 moves in the axial direction, the coil spring 5 between the movable cam 100 and the clutch ring 30 is compressed in the axial direction, and the elastic force is accumulated. When the compression force overcomes the elastic force of the coil spring 4 between the clutch ring 30 and the output shaft 20, the clutch ring 30 moves in the axial direction and approaches the output shaft 20.

  Like the movable cam 100, the clutch ring 30 is also concavo-convexly fitted to the input outer ring 10 with a concave groove 18 (see FIG. 2B) and a convex portion 32 (see FIGS. 5A and 5B). Therefore, it rotates with the input outer ring 10.

  Therefore, the clutch ring 30 meshes with the output shaft 20 when the meshing phase between the dog 34 of the clutch ring 30 and the dog 83 of the output shaft 20 matches due to the rotation and axial movement of the clutch ring 30. Thereby, the rotational torque of the input outer ring | wheel 10 is transmitted to the output shaft 20 via the clutch ring 30, and a door can be opened and closed electrically.

  At this time, as described above, the movable cam 100 rotates with the input outer ring 10, and the fixed cam 90 receives the rotational force from the movable cam 100 and rotates the same against the rotational resistance of the wave washer 6. Since the rotation resistance by the wave washer 6 is received from the cover 50 which is a member, the fixed cam 90 transmits the axial force to the movable cam 100 by the rotation resistance by the wave washer 6.

  In the two-way clutch unit, the dogs 34 and 83 of the dog clutch 2 are engaged with each other to the innermost part in the state of power transmission from the input outer ring 10 to the output shaft 20 between the elastic force of the coil spring 4 and the elastic force of the coil spring 5. I try to balance in the state. FIG. 10 compares the dog meshing state in the dog clutch between the embodiment of the present invention (the product of the present invention in FIG. 1) and the conventional example (the conventional product in FIG. 11). It is a graph which shows the relationship of the spring load with respect to a horizontal axis | shaft and a dog clearance gap (vertical axis). Here, the “dog gap” shown on the vertical axis means an axial gap between the dog tip of the clutch ring and the dog tip of the output shaft.

  In both of the present invention product and the conventional product, the coil spring 5 (170) between the movable cam 100 (144) and the clutch ring 30 (130) is compressed in the axial direction by the movement of the movable cam 100 (144) in the axial direction. Accumulated. When the compression force overcomes the elastic force of the coil spring 4 (190) between the clutch ring 30 (130) and the output shaft 20 (120), the clutch ring 30 (130) moves in the axial direction (the left side in FIGS. 1 and 11). ) To approach the output shaft 20 (120) and stop when the tips of the dogs 34, 83 (182, 184) of the dog clutch 2 (180) abut against each other.

  When the meshing phase of the dog 34 (184) of the clutch ring 30 (130) and the dog 83 (182) of the output shaft 20 (120) are matched by the rotation of the clutch ring 30 (130), the coil spring 4 (190 ), The clutch ring 30 (130) further moves in the axial direction by the elastic force of the coil spring 5 (170) in a state of overcoming the elastic force of the dog clutch 2 (180). Dogs 34 and 83 (182 and 184) mesh with each other. In the meshed state of the dogs 34 and 83 (182 and 184) in the dog clutch 2 (180), the elastic force of the coil spring 4 (190) and the elastic force of the coil spring 5 (170) are balanced.

In the conventional product, the spring load of the coil spring 170 is increased until the tips of the dogs 182 and 184 are abutted until the clutch ring 130 comes close to the output shaft 120 and the tips of the dogs 182 and 184 of the dog clutch 180 abut each other. The position at which the clutch ring 130 stops at time is the position X ₁ in the figure.

When the meshing phase between the dog 182 and 184 of the dog clutch 180 matches, further since the clutch ring 130 is close to the output shaft 120, and the stopping position X ₁ of the clutch ring 130 as a boundary, the spring load of the coil spring 170 Decreases, and the elastic force of the coil spring 190 and the elastic force of the coil spring 170 are balanced at the intersection X ₂ with the spring load of the coil spring 190.

  At this time, in the conventional product, the dogs 182 and 184 in the dog clutch 180 are not in a state of being engaged to the innermost part (see point A in the figure). That is, there are gaps between the dog 184 of the clutch ring 130 and the facing surface of the output shaft 120 and between the dog 182 of the output shaft 120 and the facing surface of the clutch ring 130.

On the other hand, in the product of the present invention, the spring load of the coil spring 5 increases until the clutch ring 30 comes close to the output shaft 20 and the tips of the dogs 34 and 83 of the dog clutch 2 abut against each other. The position at which the clutch ring 30 stops when the tips of 34 and 83 come into contact with each other is set to the position Y _{1 in the} figure by increasing the stroke of the coil spring 5 as compared with the conventional product.

When the meshing phases of the dogs 34 and 83 of the dog clutch 2 coincide with each other, the clutch ring 30 further approaches the output shaft 20, so that the spring load of the coil spring 5 is bordered on the stop position Y ₁ of the clutch ring 30. And the elastic force of the coil spring 4 and the elastic force of the coil spring 5 are balanced at the intersection point Y ₂ with the spring load of the coil spring 4. The coil spring 4 in the product of the present invention is equivalent to the coil spring 190 of the conventional product.

  At this time, in the product of the present invention, the dogs 34 and 83 in the dog clutch 2 are engaged with each other to the innermost part (see point B in the figure). That is, between the dog 34 of the clutch ring 30 and the facing surface 85 of the output shaft 20 (see FIGS. 4A and 4B), and between the dog 83 of the output shaft 20 and the facing surface 31 of the clutch ring 30 [FIG. a) and (b)] are not present.

  In this way, the elastic force of the coil spring 4 and the elastic force of the coil spring 5 are balanced in a state where the dogs 34 and 83 of the dog clutch 2 are engaged with each other to the innermost part, so that the load shaft can output to the output shaft 20. Even if the output shaft 20 is tilted with respect to the clutch ring 30 with respect to the moment load that cannot be supported by the rolling bearing 1, the elastic force of the coil spring 4 and the elastic force of the coil spring 5 are balanced. That is, when the dogs 34 and 83 are engaged with each other in the dog clutch 2 constituted by the output shaft 20 and the clutch ring 30, the dogs 34 and 83 are engaged with each other to the innermost part. It is possible to prevent incomplete meshing. As a result, the clutch ring 30 and the output shaft 20 can be reliably engaged and disengaged, and the operation stability of the clutch can be ensured.

  In the above-described embodiment, the case where the clutch unit is incorporated in the electric sliding door device in the one-box car has been described. The present invention can be applied to an apparatus having a specification for switching between electric and manual in an open / close mechanism such as an electric back door, an electric curtain, and an electric shutter.

  The present invention is not limited to the above-described embodiments, and can of course be implemented in various forms without departing from the scope of the present invention. The scope of the present invention is not limited to patents. It includes the equivalent meanings recited in the claims, and the equivalent meanings recited in the claims, and all modifications within the scope.

It is sectional drawing which shows the whole structure of a 2 way clutch unit in embodiment of this invention. 1A is a left side view of FIG. 1B and FIG. 1B is a cross-sectional view taken along line AA of FIG. It is a shaft member of the output shaft of Drawing 1, (a) is a sectional view which meets a BB line of (b), and (b) is a right view of (a). It is a dog member of the output shaft of Drawing 1, (a) is a sectional view which meets a CC line of (b), and (b) is a right side view of (a). In the clutch ring of FIG. 1, (a) is a left side view of (b), and (b) is a cross-sectional view taken along line DD of (a). 1A is a left side view of FIG. 1B and FIG. 2B is a cross-sectional view taken along line EE of FIG. It is a movable cam of the cam mechanism of FIG. 1, (a) is sectional drawing which follows the FF line of (b), (b) is a right view of (a). 1A is a left side view of FIG. 1B, and FIG. 1B is a cross-sectional view taken along line GG of FIG. 1A is a left side view of FIG. 1B, and FIG. 1B is a cross-sectional view taken along line HH of FIG. FIG. 5 is a graph comparing the meshing state of the dog in the dog clutch between the present invention product and the conventional product, and showing the relationship between the spring load and the dog clearance with respect to the axial movement amount of the clutch ring. It is sectional drawing which shows the whole structure of the conventional 2 way clutch unit.

Explanation of symbols

1 Rolling bearing 2 Dog clutch 4 First elastic member (coil spring)
5 Second elastic member (coil spring)
10 Input system rotating member (input outer ring)
20 Output system rotating member (output shaft)
30 Torque transmission member (clutch ring)
34 Dog 40 Control member (cam mechanism)
51 Static system member (housing)
83 Dog

Claims (6)

  A stationary system member, an input system rotational member that is rotationally driven by a drive source, an output system rotational member that extracts torque transmitted from the input system rotational member, and an input system rotational member and an output system rotational member. A torque transmitting member that is axially movable between the output system rotating member and is capable of engaging / disengaging with the output system rotating member, and a torque transmitting member is moved in the axial direction through relative angular displacement with respect to the stationary system member. And a control member for controlling engagement / disengagement between the torque transmission member and the output system rotating member, and a rolling bearing is interposed between the stationary system member and the output system rotating member. Way clutch unit.   A stationary system member, an input system rotational member that is rotationally driven by a drive source, an output system rotational member that extracts torque transmitted from the input system rotational member, and an input system rotational member and an output system rotational member. A torque transmitting member that is axially movable between the output system rotating member and is capable of engaging / disengaging with the output system rotating member, and a torque transmitting member is moved in the axial direction through relative angular displacement with respect to the stationary system member. And a control member for controlling engagement / disengagement between the torque transmission member and the output system rotating member, and a dog is formed at each of the axially opposed portions of the torque transmitting member and the output system rotating member. A dog clutch that engages and disengages the dog with the output system rotating member by moving the shaft in the axial direction is formed, and the two members are separated from each other between the torque transmission member and the output system rotating member. The first elastic member to which the elastic force is urged is interposed, and the elastic force is coaxial with the elastic force of the first elastic member in a direction in which both members are separated from each other between the torque transmission member and the control member. A second elastic member that is biased above is interposed, and the dog clutch dogs mesh with the elastic force of the first elastic member and the elastic force of the second elastic member to the innermost part. 2-way clutch unit characterized by balancing.   A stationary system member, an input system rotational member that is rotationally driven by a drive source, an output system rotational member that extracts torque transmitted from the input system rotational member, and an input system rotational member and an output system rotational member. A torque transmitting member that is axially movable between the output system rotating member and is capable of engaging / disengaging with the output system rotating member, and a torque transmitting member is moved in the axial direction through relative angular displacement with respect to the stationary system member. And a control member for controlling engagement / disengagement between the torque transmission member and the output system rotation member, a rolling bearing is interposed between the stationary system member and the output system rotation member, and the torque transmission member And a dog clutch that engages and disengages the dog from and to the output system rotation member by axial movement of the torque transmission member. A first elastic member is interposed between the torque transmission member and the output system rotating member so that the elastic force is biased in a direction to separate the two members from each other, and both members are disposed between the torque transmission member and the control member. The second elastic member is arranged so that the elastic force is urged coaxially with the elastic force of the first elastic member in the direction in which the first elastic member and the second elastic member are separated from each other. A two-way clutch unit that balances the elastic force of a member in a state where the dogs of the dog clutch are engaged to the innermost part.   The two-way clutch unit according to claim 1 or 3, wherein a plurality of the rolling bearings are arranged along the axial direction of the output system rotating member.   The two-way clutch unit according to claim 1, wherein the rolling bearing is a ball bearing.   6. The apparatus according to claim 1, wherein the input system rotating member is connected to a drive motor, and the output system rotating member is connected to a door slide mechanism, so that the input system rotating member is incorporated in the electric slide door device. Way clutch unit.

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